Combined rankine and vapor compression cycles

ABSTRACT

An organic rankine cycle system is combined with a vapor compression cycle system with the turbine generator of the organic rankine cycle generating the power necessary to operate the motor of the refrigerant compressor. The vapor compression cycle is applied with its evaporator cooling the inlet air into a gas turbine, and the organic rankine cycle is applied to receive heat from a gas turbine exhaust to heat its boiler within one embodiment, a common condenser is used for the organic rankine cycle and the vapor compression cycle, with a common refrigerant, R-245a being circulated within both systems. In another embodiment, the turbine driven generator has a common shaft connected to the compressor to thereby eliminate the need for a separate motor to drive the compressor.

BACKGROUND OF THE INVENTION

This invention relates generally to organic rankine cycle systems and,more particularly, to an economical and practical method and apparatustherefor.

The well known closed rankine cycle comprises a boiler or evaporator forthe evaporation of a motive fluid, a turbine fed with vapor from theboiler to drive the generator or other load, a condenser for condensingthe exhaust vapors from the turbine and a means, such as a pump, forrecycling the condensed fluid to the boiler. Such a system as is shownand described in U.S. Pat. No. 3,393,515.

Such rankine cycle systems are commonly used for the purpose ofgenerating electrical power that is provided to a power distributionsystem, or grid, for residential and commercial use across the country.The motive fluid used in such systems is often water, with the turbinethen being driven by steam. The source of heat to the boiler can be ofany form of fossil fuel, e.g. oil, coal, natural gas or nuclear power.The turbines in such systems are designed to operate at relatively highpressures and high temperatures and are relatively expensive in theirmanufacture and use.

With the advent of the energy crisis and, the need to conserve, and tomore effectively use, our available energies, rankine cycle systems havebeen used to capture the so called “waste heat”, that was otherwisebeing lost to the atmosphere and, as such, was indirectly detrimental tothe environment by requiring more fuel for power production thannecessary.

One common source of waste heat can be found at landfills where methanegas is flared off to thereby contribute to global warming. In order toprevent the methane gas from entering the environment and thuscontributing to global warming, one approach has been to burn the gas byway of so called “flares”. While the combustion products of methane (CO₂and H₂O) do less harm to the environment, it is a great waste of energythat might otherwise be used.

Another approach has been to effectively use the methane gas by burningit in diesel engines or in relatively small gas turbines ormicroturbines, which in turn drive generators, with electrical powerthen being applied directly to power-using equipment or returned to thegrid. With the use of either diesel engines or microturbines, it isnecessary to first clean the methane gas by filtering or the like, andwith diesel engines, there is necessarily significant maintenanceinvolved. Further, with either of these approaches there is still agreat deal of energy that is passed to the atmosphere by way of theexhaust gases.

Other possible sources of waste heat that are presently being dischargedto the environment are geothermal sources and heat from other types ofengines such as gas turbine engines that give off significant heat intheir exhaust gases and reciprocating engines that give off heat both intheir exhaust gases and to cooling liquids such as water and lubricants.

In the operation of gas turbine engines, it has become a common practiceto use an air conditioning system to cool the inlet air passing to thegas turbine in order to improve efficiency thereof during the warmerambient conditions. It is also known to use the heat from the exhaustgases of a gas turbine engine in order to heat water for hot waterheating. However, the demand for hot water heating during hot ambientconditions is limited while the demand for electric power oftenincreases under those conditions.

It is therefore an object of the present invention to provide a new andimproved closed rankine cycle power plant that can more effectively usewaste heat.

Another object of the present invention is the provision for a rankinecycle turbine that is economical and effective in manufacture and use.

Another object of the present invention is the provision for moreeffectively using the secondary sources of waste heat.

Yet another object of the present invention is the provision for arankine cycle system which can operate at relatively low temperaturesand pressures.

A further object of the present invention is the provision for moreeffectively generating and using the energy of a gas turbine engine.

Still another object of the present invention is the provision for arankine cycle system which is economical and practical in use.

These objects and other features and advantages become more readilyapparent upon reference to the following descriptions when taken inconjunction with the appended drawings.

SUMMARY OF THE INVENTION

Briefly, in accordance with one aspect of the invention, a centrifugalcompressor which is designed for compression of refrigerant for purposesof air conditioning, is used in a reverse flow relationship so as tothereby operate as a turbine in a closed organic rankine cycle (ORC)system. In this way, an existing hardware system which is relativelyinexpensive, is used to effectively meet the requirements of an organicrankine cycle turbine for the effective use of waste heat.

By another aspect of the invention, a centrifugal compressor having avaned diffuser is effectively used as a power generating turbine withflow directing nozzles when used in a reverse flow arrangement.

By yet another aspect of the invention, a centrifugal compressor with apipe diffuser is used as a turbine when operated in a reverse flowrelationship, with the individual pipe openings being used as nozzles.

In accordance with another aspect of the invention, a compressor/turbineuses an organic refrigerant as a motive fluid with the refrigerant beingchosen such that its operating pressure is within the operating range ofthe compressor/turbine when operating as a compressor.

In accordance with another aspect of the invention, available waste heatfrom a gas turbine exhaust is used to drive an organic rankine cycleturbine to thereby produce power which is used, in part, to drive avapor compression cycle machine such as a centrifugal chiller to cooldown the inlet temperature of the gas turbine and thereby increase itsefficiency and capacity.

By yet another object of the present invention, both the rankine cyclesystem and the vapor compression cycle system use a common condenser.

By still another object of the present invention, a common shaft is usedfor the turbine generator of the rankine cycle system and the compressorof the vapor compression cycle system, thereby eliminating the need fora compressor motor, reducing the size of the generator and eliminatingthe need for a separate compressor assembly.

In the drawings as hereinafter described, a preferred embodiment isdepicted; however various other modifications and alternateconstructions can be made thereto without departing from the true spirtand scope of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic illustration of a vapor compression cycle inaccordance with the prior art.

FIG. 2 is a schematic illustration of a rankine cycle system inaccordance with the prior art.

FIG. 3 is a sectional view of a centrifugal compressor in accordancewith the prior art.

FIG. 4 is a sectional view of a compressor/turbine in accordance with apreferred embodiment of the invention.

FIG. 5 is a perceptive view of a diffuser structure in accordance withthe prior art.

FIG. 6 is a schematic illustration of the nozzle structure in accordancewith a preferred embodiment of the invention.

FIGS. 7A and 7B are schematic illustrations of R₂/R₁ (outside/inside)radius ratios for turbine nozzle arrangements for the prior art and forthe present invention, respectively.

FIG. 8 is a graphical illustration of the temperature and pressurerelationships of two motive fluids as used in the compressor/turbine inaccordance with a preferred embodiment of the invention.

FIG. 9 is a perceptive view of a rankine cycle system with its variouscomponents in accordance with a preferred embodiment of the invention.

FIG. 10 is a schematic illustration of an air conditioning applicationin accordance with the prior art.

FIG. 11 is a schematic illustration of the rankine cycle/vaporcompression system combination in accordance with the preferredembodiment of the invention.

FIG. 12 is a schematic illustration of the rankine cycle system portionthereof.

FIG. 13 is a schematic illustration of the combined system with a commoncondenser in accordance with the preferred embodiment of the invention.

FIG. 14 is a schematic illustration of the combination with a commondrive shaft in accordance with the preferred embodiment of theinvention.

DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring now to FIG. 1, a typical vapor compression cycle is shown ascomprising, in serial flow relationship, a compressor 11, a condenser12, a throttle valve 13, and an evaporator/cooler 14. Within this cyclea refrigerant, such as R-11, R-22, or R-134a is caused to flow throughthe system in a counterclockwise direction as indicated by the arrows.

The compressor 11 which is driven by a motor 16 receives refrigerantvapor from the evaporator/cooler 14 and compresses it to a highertemperature and pressure, with the relatively hot vapor then passing tothe condenser 12 where it is cooled and condensed to a liquid state by aheat exchange relationship with a cooling medium such as air or water.The liquid refrigerant then passes from the condenser to a throttlevalve wherein the refrigerant is expanded to a low temperature two-phaseliquid/vapor state as it passes to the evaporator/cooler 14. Theevaporator liquid provides a cooling effect to air or water passingthrough the evaporator/cooler. The low pressure vapor then passes to thecompressor 11 where the cycle is again commenced.

Depending on the size of the air conditioning system, the compressor maybe a rotary, screw or reciprocating compressor for small systems, or ascrew compressor or centrifugal compressor for larger systems. A typicalcentrifugal compressor includes an impeller for accelerating refrigerantvapor to a high velocity, a diffuser for decelerating the refrigerant toa low velocity while converting kinetic energy to pressure energy, and adischarge plenum in the form of a volute or collector to collect thedischarge vapor for subsequent flow to a condenser. The drive motor 16is typically an electric motor which is hermetically sealed in the otherend of the compressor 11 and which, through a transmission 26, operatesto rotate a high speed shaft.

A typical rankine cycle system as shown in FIG. 2 also includes anevaporator/cooler 17 and a condenser 18 which, respectively, receivesand dispenses heat in the same manner as in the vapor compression cycleas described hereinabove. However, as will be seen, the direction offluid flow within the system is reversed from that of the vaporcompression cycle, and the compressor 11 is replaced with a turbine 19which, rather then being driven by a motor 16 is driven by the motivefluid in the system and in turn drives a generator 21 that producespower.

In operation, the evaporator which is commonly a boiler having asignificant heat input, vaporizes the motive fluid, which is commonlywater but may also be a refrigerant, with the vapor then passing to theturbine for providing motive power thereto. Upon leaving the turbine,the low pressure vapor passes to the condenser 18 where it is condensedby way of heat exchange relationship with a cooling medium. Thecondensed liquid is then circulated to the evaporator/boiler by a pump22 as shown to complete the cycle.

Referring now to FIG. 3, a typical centrifugal compressor is shown toinclude an electric drive motor 24 operatively connected to atransmission 26 for driving an impeller 27. An oil pump 28 provides forcirculation of oil through the transmission 26. With the high speedrotation of the impeller 27, refrigerant is caused to flow into theinlet 29 through the inlet guide vanes 31, through the impeller 27,through the diffuser 32 and to the collector 33 where the dischargevapor is collected to flow to the condenser as described hereinabove.

In FIG. 4, the same apparatus shown in FIG. 3 is applied to operate as aradial inflow turbine rather then a centrifugal compressor. As such, themotive fluid is introduced into an inlet plenum 34 which had beendesigned as a collector 33. It then passes radially inwardly through thenozzles 36, which is the same structure which functions as a diffuser inthe centrifugal compressor. The motive fluid then strikes the impeller27 to thereby impart rotational movement thereof. The impeller then actsthrough the transmission 26 to drive a generator 24, which is the samestructure which functioned as a motor in the case of the centrifugalcompressor. After passing through the impeller 27 the low pressure gaspasses through the inlet guide vanes 31 to an exit opening 37. In thismode of operation, the inlet guide vanes 31 are preferably moved to thefully opened position or alternatively, entirely removed from theapparatus.

In the centrifugal compressor application as discussed hereinabove thediffuser 32 can be any of the various types, including vaned or vanelessdiffusers. One known type of vaned diffuser is known as a pipe diffuseras shown and described in U.S. Pat. No. 5,145,317, assigned to theassignee of the present invention. Such a diffuser is shown at 38 inFIG. 5 as circumferentially surrounding an impeller 27. Here, abackswept impeller 27 rotates in the clockwise direction as shown withthe high pressure refrigerant flowing radially outwardly through thediffuser 38 as shown by the arrow. The diffuser 38 has a plurality ofcircumferentially spaced tapered sections or wedges 39 with taperedchannels 41 therebetween. The compressed refrigerant then passesradially outwardly through the tapered channels 41 as shown.

In the application wherein the centrifugal compressor is operated as aturbine as shown in FIG. 6, the impeller 27 rotates in acounterclockwise direction as shown, with the impeller 27 being drivenby the motive fluid which flows radially inwardly through the taperedchannels 41 as shown by the arrow.

Thus, the same structure which serves as a diffuser 38 in a centrifugalcompressor is used as a nozzle, or collection of nozzles, in a turbineapplication. Further such a nozzle arrangement offers advantages overprior art nozzle arrangements. To consider the differences andadvantages over the prior art nozzle arrangements, reference is made toFIGS. 7A and 7B hereof.

Referring now to FIG. 7A, a prior art nozzle arrangement is shown withrespect to a centrally disposed impeller 42 which receives motive fluidfrom a plurality of circumferentially disposed nozzle elements 43. Theradial extent of the nozzles 43 are defined by an inner radius R₁ and anouter radius R₂ as shown. It will be seen that the individual nozzleelements 43 are relatively short with quickly narrowing cross sectionalareas from the outer radius R₂ to the inner radius R₁. Further, thenozzle elements are substantially curved both on their pressure surface44 and their suction surface 46, thus causing a substantial turning ofthe gases flowing therethrough as shown by the arrow.

The advantage of the above described nozzle design is that the overallmachine size is relatively small. Primarily for this reason, most, ifnot all, nozzle designs for turbine application are of this design. Withthis design, however, there are some disadvantages. For example, nozzleefficiency suffers from the nozzle turning losses and from exit flow nonuniformities. These losses are recognized as being relatively small andgenerally well worth the gain that is obtained from the smaller sizemachine. Of course it will be recognized that this type of nozzle cannotbe reversed so as to function as a diffuser with the reversal of theflow direction since the flow will separate as a result of the highturning rate and quick deceleration.

Referring now to FIG. 7B, the nozzle arrangement of the presentinvention is shown wherein the impeller 42 is circumferentiallysurrounded by a plurality of nozzle elements 47. It will be seen thatthe nozzle elements are generally long, narrow and straight. Both thepressure surface 48 and the suction surface 49 are linear to therebyprovide relatively long and relatively slowly converging flow passage51. They include a cone-angle ∝ within the boundaries of the passage 51at preferably less then 9 degrees, and, as will been seen, the centerline of these cones as shown by the dashed line, is straight. Because ofthe relatively long nozzle elements 47, the R₂/R₁ ratio is greater then1.25 and preferably in the range of 1.4.

Because of the greater R₂/R₁ ratio, there is a modest increase in theoverall machine size (i.e. in the range of 15%) over the conventionalnozzle arrangement of FIG. 7A. Further, since the passages 51 arerelatively long the friction losses are greater than those of theconventional nozzles of FIG. 7A. However there are also some performanceadvantages with this design. For example, since there are no turninglosses or exit flow non-uniformities, the nozzle efficiency issubstantially increased over the conventional nozzle arrangement evenwhen considering the above mentioned friction losses. This efficiencyimprovement is in the range of 2%. Further, since this design is basedon a diffuser design, it can be used in a reversed flow direction forapplications as a diffuser such that the same hardware can be used forthe dual purpose of both turbine and compressor as described above andas will be more fully described hereinafter.

If the same apparatus is used for an organic rankine cycle turbineapplication as for a centrifugal compressor application, the applicantshave recognized that a different refrigerant must be used. That is, ifthe known centrifugal compressor refrigerant R-134a is used in anorganic rankine cycle turbine application, the pressure would becomeexcessive. That is, in a centrifugal compressor using R-134a as arefrigerant, the pressure range will be between 50 and 180 psi, and ifthe same refrigerant is used in a turbine application as proposed inthis invention, the pressure would rise to around 500 psi, which isabove the maximum design pressure of the compressor. For this reason, ithas been necessary for the applicants to find another refrigerant thatcan be used for purposes of turbine application. Applicants havetherefore found that a refrigerant R-245fa, when applied to a turbineapplication, will operate in pressure ranges between 40-180 psi as shownin the graph of FIG. 8. This range is acceptable for use in hardwaredesigned for centrifugal compressor applications. Further, thetemperature range for such a turbine system using R-245fa is in therange of 100-200° F., which is acceptable for a hardware system designedfor centrifugal compressor operation with temperatures in the range of40-110° F. It will thus be seen in FIG. 8 that air conditioningequipment designed for R-134a can be used in organic rankine cycle powergeneration applications when using R-245fa. Further, it has been foundthat the same equipment can be safely and effectively used in highertemperatures and pressure ranges (e.g. 270° and 300 psia are shown bythe dashed lines in FIG. 8), thanks to extra safety margins of theexisting compressor.

Having discussed the turbine portion of the present invention, we willnow consider the related system components that would be used with theturbine. Referring to FIG. 9, the turbine which has been discussedhereinabove is shown at 52 as an ORC turbine/generator, which iscommercially available as a Carrier 19XR2 centrifugal compressor whichis operated in reverse as discussed hereinabove. The boiler orevaporator portion of the system is shown at 53 for providing relativelyhigh pressure high temperature R-245fa refrigerant vapor to aturbine/generator 52. In accordance with one embodiment of theinvention, the needs of such a boiler/evaporator may be provided by acommercially available vapor generator available from Carrier LimitedKorea with the commercial name of 16JB.

The energy source for the boiler/evaporator 53 is shown at 54 and can beof any form of waste heat that may normally be lost to the atmosphere.For example, it may be a small gas turbine engine such as a CapstoneC60, commonly: known as a microturbine, with the heat being derived fromthe exhaust gases of the microturbine. It may also be a larger gasturbine engine such as a Pratt & Whitney FT8 stationary gas turbine.Another practical source of waste heat is from internal combustionengines such as large reciprocating diesel engines that are used todrive large generators and in the process develop a great deal of heatthat is given off by way of exhaust gases and coolant liquids that arecirculated within a radiator and/or a lubrication system. Further,energy may be derived from the heat exchanger used in the turbo-chargerintercooler wherein the incoming compressed combustion air is cooled toobtain better efficiency and larger capacity.

Finally, heat energy for the boiler may be derived from geothermalsources or from landfill flare exhausts. In these cases, the burninggases are applied directly to the boiler to produce refrigerant vapor orapplied indirectly by first using those resource gases to drive anengine which, in turn, gives off heat which can be used as describedhereinabove.

After the refrigerant vapor is passed through the turbine 52, it passesto the condenser 56 for purposes of condensing the vapor back to aliquid which is then pumped by way of a pump 57 to the boiler/evaporator53. Condenser 56 may be of any of the well known types. One type that isfound to be suitable for this application is the commercially availableair cooled condenser available from Carrier Corporation as model number09DK094. A suitable pump 57 has been found to be the commerciallyavailable as the Sundyne P2CZS.

Referring now to FIG. 10, there is shown a prior art application of acentrifugal chiller as used for a cooling of the inlet air of a gasturbine engine for purposes of increasing the efficiency thereof. Thatis, the system operates in a conventional manner to circulate therefrigerant serially from the motor driven compressor 11 to thecondenser 12 a throttle valve 13 and an evaporator cooler 14. Air beingcooled, rather than being circulated to a building to be cooled, ispassed to the inlet of a gas turbine engine to thereby twist the poweroutput thereof. This occurs because of two reasons. First the efficiencyof the thermodynamic cycle is increased by the lower inlet temperatureof the inlet gas. Secondly, because the lower temperature of the inletair increases its density, and since the gas turbine compressor isessentially accosted by a flow device, the mass flow rate through thecompressor is increased. Inasmuch as the increase in power outputresulting from the use of the air conditioner in this manner is greaterthan the power required to operate the air conditioner, such anapplication maybe economically feasible. It becomes more feasible whenthe system is used in combination with a rankine cycle system inaccordance with the present invention. As will now be described inreference to FIG. 11.

Consistent with the system as described hereinabove, ambient air,indicated by an arrow 58 enters the air conditioner 59, with the cooledair then entering the gas turbine 61 as inlet air indicated by the arrow62. The power that is generated by the gas turbine then passes alongdotted line 63 to a grid 64. The exhaust gases from the gas turbine 61,which are normally at a temperature of around 700° F., are commonlydischarged to the atmosphere. In accordance with the present invention,the exhaust gases pass along ling 66 to drive a turbine 19 of an organicrankine cycle system 64 as shown in FIGS. 11 and 12. The turbine 19, inturn, drives the generator 21, with power then passing to both the airconditioner 59 and to the grid 64 by dotted lines 68 and 69,respectively. The power that is generated by the ORC system 65 from theexhaust gas of the gas turbine 61 is estimated to be 4-6 times(depending on gas turbine exhaust temperature and mass flow rate) largerthen that power required to operate the air conditioner 59 whileperforming gas turbine inlet cooling. Thus, the extra power can bepassed by grid 64 along lines 69.

Referring now to FIG. 13, there is shown a combination of the airconditioning system of FIG. 10 and the rankine cycle system of FIG. 12.However, rather then the individual condensers 12 and 18, respectively,single, common condenser 71 is provided to perform the condensingfunctions in each of the two systems. With such a combined system, it isof course, necessary to have the same medium passing from the compressor11 and the turbine 19 to the condenser 71. The refrigerant R-245a hasbeen found to be suitable for this purpose. Thus, the rankine cyclesystem described hereinabove, with the diffuser being used in reverse asa nozzle, and with R-245a as the refrigerant therefore to circulate therefrigerant through the system as indicated in FIG. 13 whereinrefrigerant would be heated at the boiler by heat from the gas turbineexhaust to a temperature of 225° F. After passing through the turbine19, the temperature of the refrigerant would be reduced to 140° F. priorto passing to the condenser 71, after which the temperature of therefrigerant would be at around 100° F. prior to being passed to theboiler to be heated.

The vapor compression cycle would be different from that describedhereinabove wherein a high pressure system using R-134a as therefrigerant as described. Here, it would be necessary to use arelatively low pressure system with the R-245a refrigerant. A suitablevapor compression system for this purpose would be based on low pressurechiller designs using, for example R-11, R-123 or R-114. With such avapor compression system, using R-245a, the temperatures of therefrigerant as it passes through the cycle would be as shown in FIG. 13.Thus, the condensed refrigerant from the condenser 71 would be around a100° F., and after passing through the throttle valve 13 would be 40° F.and at a vapor/liquid mixture of about 85% liquid and 15% vapor. Afterpassing through the evaporator 14, the refrigerant would still be 40° F.but would be entirely in the vaporous state to pass to the compressor11. The temperature of the refrigerant passing to the condenser 71 wouldthen be around 125° F.

In such a combined system, the condenser 71 would need to be slightlylarger then the condenser 18 used in the rankine cycle system by itselfas shown in FIG. 12. However, the disadvantage of the slight increase insize would be more then off set by the advantage, both in cost andspace, that results from the elimination of the condenser 12 that wouldotherwise be needed for the vapor compression cycle.

Having eliminated a condenser, a combined system can now be takenfurther to eliminate the drive motor 16 of the compressor 11 as shown inFIG. 14. Further, the turbine 19 drives the generator 21 by way of ashaft 72 with the shaft 72 then being a common shaft which extendsthrough the other end of the generator 21 to drive the compressor 11.This maybe used between the turbine and the generator, or between thegenerator and the compressor. However, a direct drive arrangement isfeasible if the components are properly selected. For example, a 400KW_(el) microturbine would produce 720 KW_(th) of waste heat that, whencaptured by the organic rankine cycle of this invention, would producean additional 80 KW_(el) net. The amount of cooling required to cool theambient air entering the 400 KW_(el) microturbine is 20 tons ofrefrigeration (=70 KW_(th)) requiring a compressor with a 15 KW_(el)motor. Specific speed considerations of the larger head/flow turbine andthe smaller head/flow compressor allows operation of identical space ona common shaft.

While the present invention has been particularly shown and describedwith reference to preferred and alternate embodiments as illustrated inthe drawings, it will be understood by one skilled in the art thatvarious changes in detail may be effected therein without departing fromthe spirit and scope of the invention as defined by the claims.

1. A combination of a rankine cycle turbine generator system and an airconditioner comprising: a rankine cycle system including a boiler, aturbine for driving a generator, a condenser and a pump, wherein saidboiler is heated from the exhaust gases of a gas turbine engine; and avapor compression system including an evaporator, a motor drivencompressor, a condenser and a throttle valve, wherein said evaporator isadapted to cool inlet air flowing to said gas turbine engine whereinsaid condenser in said rankine cycle system is common with the saidcondenser of said vapor compression system and further wherein a commonrefrigerant used in both the rankine cycle system and the vaporcompression system is an organic refrigerant.
 2. A combination of arankine cycle turbine generator system and an air conditionercomprising: a rankine cycle system including a boiler, a turbine fordriving a generator, a condenser and a pump, wherein said boiler isheated from the exhaust gases of a gas turbine engine; and a vaporcompression system including an evaporator, a motor driven compressor, acondenser and a throttle valve, wherein said evaporator is adapted tocool inlet air flowing to said gas turbine engine wherein saidcompressor drive motor receives its electrical power entirely from theturbine generator.
 3. A combination of a rankine cycle turbine generatorsystem and an air conditioner comprising: a rankine cycle systemincluding a boiler, a turbine for driving a generator, a condenser and apump, wherein said boiler is heated from the exhaust gases of a gasturbine engine; and a vapor compression system including an evaporator,a motor driven compressor, a condenser and a throttle valve, whereinsaid evaporator is adapted to cool inlet air flowing to said gas turbineengine wherein said refrigerant is R-245a.
 4. A combination of a rankinecycle turbine generator system and an air conditioner comprising: arankine cycle system including a boiler, a turbine for driving agenerator, a condenser and a pump, wherein said boiler is heated fromthe exhaust eases of a gas turbine engine; and a vapor compressionsystem including an evaporator, a motor driven compressor, a condenserand a throttle valve, wherein said evaporator is adapted to cool inletair flowing to said gas turbine engine wherein the turbine generator andsaid compressor motor comprises a single element with a common shaftinterconnecting said turbine to said compressor.
 5. A combination as setforth in claim 1 wherein said air conditioning system is a chiller.